Control apparatus



27, 1966 A. L. MALMGREN 3,293,955

CONTROL APPARATUS Filed Sept. 23, 1964 I5 Sheets-Sheet 1 FIG. E

FIG. 5

I NVENTOR. ARTHUR L. MALMGREN BY mAL ZZ LJ ATTORNEY v Dec. 27, 1966 A. L. MALMGREN 3,293,955

CONTROL APPARATUS Filed Sept. 23, 1964 S Sheets-Sheet 2 INVENTOR ARTHUR L. MALMGREN ATTORNEY Dec. 27, 1966 3 Sheets-Sheet :3

Filed Sept. 23, 1964 FIG. 3

FIG. 6

N Am Rm 5: mm OM w W. 0% TN. mm W L I m fi U H m l .m w 5 M m 6 w Y M B 2 5 M m IL! w 3 O l B m M 2 I c r$m 0 PS ATTORNEY United States Patent 3,293,955 CONTROL APPARATUS Arthur L. Malmgren, Seattle, Wash, assignor to Honeywell linc., Minneapolis, Minn., a corporation of Delaware Filed Sept. 23, 1964, Ser. No. 398,692 6 Claims. (Cl. 77-77) This invention relates to a perforating apparatus and more particularly concerns a perforating apparatus involving a rotating, air-turbine driven, air-bearing mounted, air-piston actuated tape cutter.

Extensive efforts are currently being made to increase the speed of processing digital information. Perforated tape is an important medium for data processing but has a dis-advantage that stems from the upper limits of speed of preparation. The present upper limit for tape perforators in the 300*500 characters per second range. Often reliable and economic designs restrict this range even further. Over-all processing system designs can be functionally and economically improved if higher speed tape perforators are available. Usually in high speed data links the data is originally stored magnetically before tape punching or page copy preparation because perforators are too slow for direct connection to the data link. This introduces delays and manual handling requirements and increased equipment costs. To overcome the speed limitations of conventional mechanical linkage and cam assemblies used for punching tape, the present invention operates wit-h less force than is norm-ally necessary, by rotating the punching die and also reduces the inertia in the mechanism by applying the moving force pneumatically thereby eliminating the inertia found in the force applying mechanism of the prior art. Furthermore, the intricate mechanical punches presently available are more subject to failure than the relatively simple perforator of the present invention. The approach used in the pneumatic perforator, or punch, based On well developed fundamental techniques constitutes an advance in the state of the art and provides the answer to many existing data processing problems.

Accordingly, it is an object of this invention to provide a high speed tape punching mechanism employing a rotating die and a pneumatically actuated mechanism to reduce inertia and force requirements and thus increase speed of operation.

Other objects and advantages of this invention will become apparent in the following description and in the drawings in which:

FIGURE 1 is a cross-sectional View of the perforator mechanism;

FIGURE 2 is a sectional view of the perforator mec anism housing;

FIGURE 3 is an isometric view of a punch-cutter pis ton and hit;

FIGURE 4 is a partial cross sectional view of the punching-cutting end of a punch bit adapted to be replaceable;

FIGURE 5 is a partial cross sectional view of a bistable electrostrictive bender bar exhaust valve; and

FIGURE 6 shows a schematic representation of a system employing the punch mechanism.

In describing the embodiment of the invention illustrated in the drawings specific terms will be used for clarity. Limitation to the specific terms is not intended and it is to he understood that all specific terms include all technical equivalents that operate in a similar manner to accomplish a similar end. Furthermore, the size of the elements shown in the figures has been enlarged several times for clarity.

Referring now to FIGURES 1, 2 and 3, there is shown a punch-cutter housing member 10 and a punch-cutter member or piston 12. Piston 12 is divided into an upper and a lower portion by a reduced diameter shank or central portional 16. Part of the upper portion of piston 12 forms a turbine wheel 17. With the shank 16 reduced in diameter, piston 12 has upper and lower surface areas or shoulders 18 and 20 respectively. A reduced diameter end on the lower portion of piston 12 forms a punch-cutter bit 22 that is hollow ground to form dynamically balanced punch-cutter tips 24 and 26. To provide ease of production, the punching-cutting tips 24 and 26 may, as shown in FIGURE 1, be circular so that its shape appears as the result of the intersection of two circular cylinders at right angles to each other. The cutter bit 22 may be ground from tungsten carbide for maximum life and may or may not be replaceable depending upon the particular application. The rest of the piston 12 may be made of steel or some lighter material such as berryllium to further reduce inertia.

The housing 10 is shaped to have a rib 28 forming a chamber 29 proximate the shank 16 and upper and lower chambers 30 and 32 proximate the upper and lower port-ions of piston 12 respectively. The upper, lower and shank portions of piston 12 are normally positioned in their respective chambers 30, 32 and 29 with only slight clearance space. Air flowing in the clearance space operates to provide an air bearing for rotation of piston 12 as will be described. Horizontal surfaces 38 and 40 of rib 23 together with shoulders 18 and 20 of piston 12 define the horizontal boundaries of two pressure chambers 42 and 44 respectively.

Adjacent the turbine wheel 17 in the wall of upper chamber 30 are diametrically opposed input port 46 and output port 48. High pressure air is injected into port 46 through nozzle 50 which is connected to an external source of high pressure lair via passage 52 and connector 53 in housing 10. High pressure air injected into port 46 impinges on turbine wheel 17 producing high speed rotation of piston 12. After impinging on turbine wheel 17 and losing most of its kinetic energy, the air is exhausted through output port 48 to a point external to the housing 10 via a nozzle 54 and a passage 56.

An external high pressure air supply is also connected to a passage 58 by a connector 5% in housing 10. Passage 58 divides into two branch passages 60 and 62 that terminate or open into chambers 42 and 44 respectively.

Also opening into pressure chamber 42 at a point near the intersection of surface 38 with the side wall of upper chamber 30 is an exhaust passage 64 in housing 10 leading to a port 66 that opens into a secondary chamber 68 defined by housing 11). An exhaust port 70, in a wall of chamber 68, is the termination of an exhaust passage 72 in housing 10 that leads to the exterior of housing 10.

An exhaust passage 74 in housing 10, corresponding to passage 64, opens into pressure chamber 44 at a point in the side wall of lower chamber 32, and slightly below the intersection of surface 40 and the side wall of chamber 32. Passage 74 terminates in a port 76 slightly and directly below port 66, in a wall of chamber 68.

Ports 66 and '76, during normal operation of the perforator mechanism, are selectively, but not independently, opened and closed. If port 66 is fully open, then port 76 is fully closed, and conversely. A bistable exhaust valve 78 is cantilever-supported in a wall of chamber 68 opposite the ports 66 and 76. Valve 78 is an electrostrict-ive bender bar that bends upward of downward depending upon the polarity of an applied electric field. In the position shown in FIGURE 1 the bender bar is relaxed and covers port 66. Upon application of an electric field of the proper polarity the bender bar will bend down to cover port 76. The bender bar is composed of two oppositely polarized wafers, 78a and 78b better shown in FIGURE 5, bonded together, that expand and contract respectively when a field is applied, thereby causing a bending action. One end of the valve 78, including electrical terminals 80, 82 and conductors 84 and 86, is mounted in the wall of chamber 68 thereby providing cantilever-support. Conductors 84 and 86 are brought out to the exterior of housing 10 through sealed passage 90 in housing 10.

There are two other exhaust passages 92 and 94 communicating with pressure chambers 42 and 44. Passage 92 terminates in a pout 96 opening on the side wall of upper chamber 30 at a point slightly above the opening of passage 64 into chamber 42. In a corresponding manner passage 94 terminates in port 98 opening on the side wall of lower chamber 32 at a point slightly below the opening of passage 74 into chamber 44.

FIGURE 4 shows the details of a replaceable punching-cutting bit. The punch-cutter bit 22 is inserted into a bore 100 in the lower portion of piston 12. The bore 100 is lined with a plastic sleeve 102. To change bits, shank 22 is simply pulled out and a new bit is pressed in place by hand pressure.

FIGURE 5 shows the bender bar 78 and the surrounding walls of chamber 68 in cross-sectional view. Bender bar 78 is shown composed of the two wafers 78a and 78b bonded together by a layer of bonding material 79. The bonded arrangement is known as a bimorph. The polarization of wafers 78a and 78b is arranged so that a single applied electric field simultaneously causes one wafer to expand and the other to contract thereby causing bending. There are many ways of polarizing the wafers that are well-known in the art.

FIGURE 6 shows a system utilizing the punch of the present invention. In FIGURE 6 a pressure source 110 feeds high pressure fluid such as air to the punch 10 through conduits 112 and 113 which are connected to the connectors 53 and 54 [respectively (shown in FIG- URE l). The punch housing 10 is shown in FIGURE 6 located above a tape 120 which is to be punched in accordance with signals from a data source 125 which may be a digital computer, for example. An out-put from source 125 appears on a line 127 whenever a punch operation is desired. Line 127 is connected to punch 10 so as to present the signal to the bender bar valve 78 by way of conductors 84 and 86 (FIGURE 1). This instigates the punching action as will be explained.

Also connected to source 125 in FIGURE 6 by way of a line 130 is a stepping motor 133. Signals from source 125 on line 130 are 180 out of phase with any signals which might appear on line 127 and are continuous so that mot-or 133 steps continuously between punching operations.

Motor 133 is connected to a tape drive sprocket 140 by a mechanical connection shown as dashed line 142. Tape 120 will move in steps under the action of motor 133 and will be still for predetermined dwell periods after each step. During this dwell period any signals on line 127 will operate the punch 10. Upon operation, the bit 22 will pass from punch 10 through the tape 120 to a backing die 145 and return after which action motor 133 will continue stepping and tape 120 will continue to progress. When it is desired to punch a plurality of holes crosswise of tape 120 to form a standard digital configuration, a plurality of punch units corresponding to punch 10 may be placed side by side and on both sides of the tape, if desired, with each being independently operated from the source 125. Also the sprocket holes utilized by sprocket 140 to drive the tape may be punched by one or more punches corresponding to punch 10.

Referring again to FIGURE 1 the control of the perforating mechanism during a cycle of operation will now be explained. The high pressure air supply is connected to passage 58, from which the high pressure air is directed through passages 60 and 62 to the pressure chambers 42 and 44 in such a manner that an average upward force is produced holding piston 12 in a rest position shown in FIGURE 1. This is accomplished by the location of the exhaust porting and the position of the bistable exhaust valve 78. In the position shown in FIGURE 1, high pressure air injected into pressure chamber 42 through passage 60 is partially exhausted out port 96 and passage 92. However, port 96 is nearly blocked by piston 12, resulting in a relatively high pressure in chamber 42. Note that exhaust passage 64 in the rest position is blocked by the bistable exhaust valve 78. On the other hand high pressure air injected into pressure chamber 44 through passage 62 is more readily exhausted because the lower portion of piston 12 blocks off a relatively small part of the opening to passage 74 so that the pressure in chamber 40 is relatively low. It is this differential pressure that holds the piston 12 in rest position.

To move piston 12 downward valve 78 is actuated by a control signal so as to bend downward to block port 76 and open port 66. When this occurs pressure in chamber 42 is reduced because of the increased exhaust through passage 64, port 66, port 70, and exhaust passage 72 to the exterior of housing 10. At the same time, pressure in chamber 44 increases because of the blocking of port 76. As the pressure builds up in the chamber 44 the piston moves downward and the spinning bit cuts the tape. The downward motion continues until the lower portion of piston 12 uncovers port 98 and passage 94. At this time the pressure in chamber 44 decreases and the piston comes to rest in the extended position. To remove the cutting scrap when the cutting operation has occurred a longitudinal port extending from the bottom of cutter bit 22 upwards through piston 12 and terminating with holes proximate the blades of turbine 17 may be employed. Air would flow through port 53 through these holes, down the piston 12 and out the bottom of the cutter bit 22 to blow the cutting scrap away. To complete the cycle the signal causing bender bar 78 to bend down is removed and the bender bar returns to its normal position covering port 66 and opening port 76. The pressure in chamber 42 again increases moving the piston 12 upward until port 96 and passage 92 begin to be uncovered, decreasing somewhat the air pressure in chamber 42 and bringing the piston to rest in the retracted position. The position of port 96 is closed so that in the balanced rest position piston 12 does not come into frictional contact with the upper wall of chamber 30 of housing 10.

At the same time that piston 12 is moving up and down it is also rotating at high speed because of the high pressure air driving turbine wheel 17. Air escaping between various portions of the piston walls and the walls of the upper and lower chambers 30 and 32 serves as an air bearing, as does the air between shank 16 of piston 12 and Ii 28.

Relatively high leakage of valve 78 can be tolerated because the system operates on pressure differential rather than absolute pressures.

From the foregoing description many advantages of the invention can be seen. It is seen that a minimum force is required for punching because the piston 12 is rotating. This means that to a large extent the tape will be cut rather than punched as the rotating piston 12 is lowered. Much of the energy for the cutting action comes from turbine 17 rather than from the vertical piston movement and the force controlling the vertical displacement needs to overcome only the inertia of the piston 12 and the small frictional forces of the air bearing.

Since there need be no mechanical contacts within the mechanism the problems of wear, lubrication, heating, and adjustment will be reduced to a minimum. The high rotation possible with air-turbines and bearings allow a hole to be cut in a very short time by the two tooth cutter tip. These factors permit tape perforations at speeds well beyond those possible with convention punching mechanisms.

It is to be understood that variations may be made in the details. The air-bearing may take one of many particular forms for example an air step bearing, or a multiple orifice bearing. The particular cutter bit configuration may be varied and different methods of piston control with feedback can be used along with different types of valves. The electrostrictive valve has merely been shown as one practical method of rapid valving. These and other changes or variations can be made without departing from the spirit or scope of the invention as defined by the appended claims.

I claim:

l. A pneumatic perforator in combination with a source of air under pressure and connection means, comprising:

a piston with a longitudinal axis of rotation having an upper end adapted to function as a turbine wheel, a lower end hollow ground to provide two dynamically balanced cutting tips, and a central region reduced in diameter providing upper and lower surface areas normal to the axis of rotation;

a housing defining a cylinder for said piston and dividing the area surrounding the central region of said piston into upper and lower piston actuator cavities, adjacent surface areas of said piston and said housing between said upper and lower cavities defining an air bearing, said housing also defining a chamber having an exhaust passage to the exterior of said houss;

means defined by said housing for supplying high pressure air to the upper and lower piston actuator cavities from said air source thereby providing forces acting on the upper and lower normal surface areas to cause longitudinal displacement of said piston in said cylinder;

means defined by said housing for supplying air from said source in an impinging high pressure stream to a portion of said piston adapted to function as a turbine wheel;

means defined by said housing providing a first pair of air exhaust capillaries connecting the upper and low- Zr piston actuator cavities respectively to said chaman exhaust valve mounted in said chamber, selectively operable to close either one of the first pair of exhaust capillaries; and

a second pair of exhaust capillaries defined by said housing connecting the upper and lower piston actuator cavities respectively to the exterior of said housing, said second pair of exhaust capillaries alternately opened and closed by bidirectional longitudinal displacement of said piston.

2. Apparatus for continuously perforating tape comprising, in combination:

a perforator punch with a longitudinal axis of rotation having a portion adapted to function as a turbine wheel, a lower end adapted to provide dynamically balanced cutting tips, and a region reduced in di ameter thereby providing upper and lower surface areas normal to the axis of rotation;

a housing for said punch dividing the space surrounding the central region of said punch into upper and lower punch actuator cavities, adjacent surface areas of said punch and housing between the upper and lower cavities defining an air bearing;

a source of air under pressure;

a passage defined by said housing to direct an impinging stream of air on the portion of said punch adapted to function as a turbine wheel, said passage adapted to be supplied from said air source;

a first pair of passages defined by said housing to supply air to the upper and lower punch actuator cavities, respectively, adapted to be connected to said air source, the air so supplied providing longitudinal forces acting on the upper and lower normal surface areas; v

a second pair of passages defined by said housing connecting the upper and lower punch actuator cavities respectively to the exterior of said housing, for exhausting said cavities;

a source of electrical signal energy;

an electromechanical exhaust valve mounted proximate said second pair of passages selectively operable by the energy of said electrical source to block either one of the second pair of passages;

a third pair of passages defined by said housing connecting the upper and lower cavities respectively, to the exterior of said housing, said third pair of passages alternately opened and closed by longitudinal displacements of said punch, for exhausting said cavities;

a die held in spaced relationship with said housing adapted to receive said punch when the punch is in an extended perforating position; and

tape transport means operating in synchronism with the longitudinal displacements of said punch for transporting a tape to be punched, along a path between said housing and said die.

3. A high speed pneumatic paper tape perforator,

comprising, in combination:

a perforator piston with a longitudinal axis of rotation having first, second, and third regions, the first region adapted to function as a turbine wheel, the second region adapted to provide a dynamically balanced cutting tip, and the third region having a reduced diameter to provide first and second surface areas normal to the axis of rotation at the junctions of the first and second regions with the third region respectively;

a housing defining a piston cylinder, that divides the space surrounding the central region of the piston into first and second piston actuator cavities, adjacent surface areas of said piston and said cylinder between the upper and lower cavities defining an air bearing;

a pneumatic pressure source;

a passage defined by said housing, adapted to be connected to said pressure source, for causing a stream of air to impinge on the first region of said piston adapted to function as a turbine wheel, and for exhausting the air to the exterior of said housing;

a first pair of passages defined by said housing, adapted to be connected to said pressure source, for supplying air to the first and second piston actuator cavities respectively, the air so supplied providing longitudinal forces acting on the upper and lower normal surface areas;

a second pair of passages defined by said housing connecting the first and second piston actuator cavities, for exhausting said cavities;

a source of electrical signal energy;

an electromechanical valve mounted proximate said second pair of passages and selectively energized by said source to block one of the second pair of passages;

a third pair of passages defined by said housing connecting the upper and lower piston actuator cavities, respectively, to the exterior of said housing, said third pair of passages alternately opened and closed 'by longitudinal displacements of said piston, for exhausting said cavities;

a backing die plate held in spaced relationship with said housing adapted to receive the lower end of said piston, adapted to provide a cutting tip, when the piston is in an extended perforating position; and

tape transport means operating in synchronism with longitudinal displacements of said piston for transporting a tape to be perforated, along a path between said housing and said backing die plate.

4. Apparatus for selectively punch cutting a laminar material comprising:

a source of fluid under pressure;

a housing defining a chamber;

a piston positioned in the chamber for rotational movement about an axis and for movement along the axis to first and second positions, said piston including a cutting bit movable with said piston and which extends to a cutting position when the piston is in the first position and retracts from the cutting position when the piston is in the second position, said piston also including a rotation motive portion and first and second faces;

port means within said housing connected to said source of fluid and being operable to supply and exhaust fluid to and from the chamber, said port means causing fluid to pass the rotation motive portion of said piston to produce rotation of said piston about the axis, said port means also supplying fluid contiguous the first and second faces of said piston, the fluid being operable to exert pressure on the first and second faces to tend to move said piston to the first and second positions;

valve means connected to said port means and operable in accordance with a control signal to selectively change the pressure on the first and second faces to move said piston to the first and second positions;

control means connected to said valve means to supply the control signal thereto; and

material moving means connected to said housing and being operable to move the laminar material past the cutting bit, a control signal from said control means causing said valve means to change the pressure on the first of the faces of said piston thereby moving said piston to the first position so that the cutting bit moves to the cutting position and perforates the material.

5. Apparatus for selectively punch cutting a laminar material comprising, in combination:

a housing defining a chamber;

a piston positioned in said chamber, said piston in cluding a cutting bit, a turbine blade, and first and second faces, said piston being movable in said chamber between first and second positions to cause the cutting bit to move to and from a cutting position;

means moving the laminar material past the cutting position of the cutting bit;

port means in said housing for supplying and exhausting fluid to and from the chamber, said port means being operable to supply fluid flow past the turbine blade of said piston to cause rotation of the cutting bit, said port means also being operable to supply fluid pressure contiguous the first and second faces of said piston to develop forces on said piston tending to move the cutting bit to and from the cutting position; and

valve means connected to said port means, said valve means being operable to selectively change the pressure supplied contiguous the first and second faces of said piston to bring the cutting bit into and out of the cutting position, the cutting bit in the cutting position being operable to perforate the laminar material.

6. In combination:

a housing defining a chamber;

a piston having an axis, said piston being positioned in the chamber for rotational movement about the axis and for movement along the axis to first and second positions, said piston having first and second faces;

means for providing rotational movement of said piston about the axis;

port means in said housing for supplying pressure contiguous the first and second faces of said piston to produce first and second forces on said piston tending to move said piston to the first and'second positions respectively;

means connected to said first port means for selectively changing the pressure supplied contiguous the first and second faces of said piston to cause said piston to move to the first and second pistons;

additional port means in said housing for dissipating any pressure impinging upon said first and second faces of said piston when said piston has traveled a desired distance; and

an air bearing between said housing and said piston supporting said piston.

References Cited by the Examiner UNITED STATES PATENTS 2,152,293 3/1939 Wagner 77--33.5 X 2,382,526 8/1945 White 2532 3,101,014 8/1963 Rowe et a1. 7733.5 3,124,016 3/1964 Reaser 77--33.5 3,124,979 3/1964 Macks 7733.5

FRANCIS S. HUSAR, Primary Examiner. 

1. A PNEUMATIC PERFORATOR IN COMBINATION WITH A SOURCE OR AIR UNDER PRESSURE AND CONNECTION MEANS, COMPRISING: A PISTON WITH A LONGITUDINAL AXIS OF ROTATION HAVING AN UPPER END ADAPTED TO FUNCTION AS A TURBING WHEEL, LOWER END HOLLOW GROUND TO PROVIDE TWO DYNAMICALLY BALANCED CUTTING TIPS, AND A CENTRAL REGION REDUCED IN DIAMETER PROVIDING UPPER AND LOWER SURFACE AREAS NORMAL TO THE AXIS OF ROTATION; A HOUSING DEFINING A CYLINDER FOR SAID PISTON AND DIVIDING THE AREA SURROUNDING THE CENTRAL REGION OF SAID PISTON INTO UPPER AND LOWER PISTON ACTUATOR CAVITIES, ADJACENT SURFACE AREAS OF SAID PISTON AND SAID HOUSING BETWEEN SAID UPPER AND LOWER CAVITIES DEFINING AN AIR BEARING, SAID HOUSING ALSO DEFINING A CHAMBER HAVING AN EXHAUST PASSAGE TO THE EXTERIOR OF SAID HOUSING; MEANS DEFINED BY SAID HOUSING FOR SUPPLYING HIGH PRESSURE AIR TO THE UPPER AND LOWER PISTON ACTUATOR CAVITIES FROM SAID AIR SOURCE THEREBY PROVIDING FORCES ACTING ON THE UPPER AND LOWER NORMAL SURFACE AREAS TO CAUSE LONGITUDINAL DISPLACEMENT OF SAID PISTON IN SAID CYLINDER; MEANS DEFINED BY SAID HOUSING FOR SUPPLYING AIR FROM SAID SOURCE IN AN IMPINGING HIGH PRESSURE STREAM TO A PORTION OF SAID PISTON ADAPTED TO FUNCTION AS A TURBINE WHEEL; MEANS DEFINED BY SAID HOUSING PROVIDING A FIRST PAIR OF AIR EXHAUST CAPILLARIES CONNECTING THE UPPER AND LOWER PISTON ACTUATOR CAVITIES RESPECTIVELY TO SAID CHAMBER; AN EXHAUST VALVE MOUNTED IN SAID CHAMBER, SELECTIVELY OPERABLE TO CLOSE EITHER ONE OF THE FIRST PAIR OF EXHAUST CAPILLARIES; AND A SECOND PAIR OF EXHAUST CAPILLARIES DEFINED BY SAID HOUSING CONNECTING THE UPPER AND LOWER PISTON ACTUATOR CAVITIES RESPECTIVELY TO THE EXTERIOR OF SAID HOUSING, SAID SECOND PAIR OF EXHAUST CAPILLARIES ALTERNATELY OPENED AND CLOSED BY BIDIRECTIONAL LONGITUDINAL DISPLACEMENT OF SAID PISTON. 